Electromagnetic valve system

ABSTRACT

Systems are provided for electromagnetic actuation of a valve mechanism. A valve is linearly moveable between a first closed position and a second open position. A first spring is compressed when the valve is in the first closed position, and a second valve spring is compressed when the valve is in the second open position. An electromagnetic actuation assembly and a permanent magnet is combined with the valve, such that the valve is latchable in either a closed or open position, and is readily movable between positions through application of energy to the electromagnetic circuitry. The electromagnetic circuitry is controllable to increase or decrease the local magnetic flux, such as to promote movement of the valve, or to provide a soft landing of the valve at either end of movement. Some system embodiments provide energy recovery, feed back, and/or feed forward sensing and control. The electromagnetic valve system can be implemented for a wide variety of engines, valves and actuators, such as for variable valve timing, valve disablement, and/or hybrid engine and energy storage applications.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims priority to U.S. Provisional Patent ApplicationNo. 60/490,195, filed 25 Jul. 2003, which is incorporated herein byreference.

This application is also a Continuation in Part of U.S. application Ser.No. 10/674,743, filed 29 Sep. 2003, which claims priority to U.S.Provisional Patent Application No. 60/417,264, filed 9 Oct. 2002, whichis incorporated herein by reference.

FIELD OF THE INVENTION

The invention relates to the field of internal combustion engines. Moreparticularly, the invention relates to a structure and process for thecontrolled movement, latching and/or disablement valves.

BACKGROUND OF THE INVENTION

The poppet valve driven by a camshaft has bee used in internalcombustion engines for many years. Modifications to the valve train havebeen developed to permit changing the valve timing while the engine isin operation. When the timing control prevents the valves from openingduring an engine cycle, the cylinder is disabled, and the effect of avariable displacement engine is obtained. The advantage of a variabledisplacement engine is that when less than maximum efficiency power isrequired, some of the cylinders may be disabled and the remaining activecylinders' power is increased so that they will operate at greaterefficiency, while the engine output remains constant. This approach hashad limited success in practice because the usual control activates ordeactivates half the number of cylinders, and this abrupt change inoutput torque causes poor drivability. Furthermore, the disablingmechanism is relatively slow acting, so that more than one revolution ofthe crankshaft is required to make the change.

While some electromagnetic valve mechanisms have been implemented tooperate valves, the energy required to operate the system is typicallyprohibitive. Energy is often required to retain a valve in either anopen or a closed position. Furthermore, the mass of the valve train insuch systems is typically substantial, and the movement and landing ofcomponentry is often problematic.

D. Moyer, Cam Activated Electrically Controlled Engine Valve, U.S. Pat.No. 6,302,069, 16 Oct. 2001, describes “an engine valve controlresponsive to electrical signals from a controller to open and close avalve. Power to move the valve comes from a camshaft. A disabler springis compressed by a cam lobe and held compressed by its solenoid whilethe valve is held from opening by its solenoid. When the valve solenoidreleases the valve, a half oscillation between the disabler spring andvalve spring opens the valve and the valve solenoid than holds it open.The disabler solenoid then releases the disabler spring. When the valvesolenoid releases its spring, a half oscillation of the two springscloses the valve with a soft landing. The valve operation is very fast,independent of engine speed, and can be controlled over 630 crankshaftdegrees. The camshaft may run at crankshaft speed with valve disablementduring compression and expansion strokes for 4 stroke operation. 2stroke operation may be used for compressor and air motor operation as apneumatic hybrid engine.”

D. Moyer, Fast Acting Engine Valve Control with Soft Landing, U.S. Pat.No. 6,302,068, 16 October 2001, describes “an engine valve controlresponsive to electrical signals from a controller to open and closevalves. Power to move the valves comes from a conventional camshaft. Adisabler spring is compressed by a cam lobe and held compressed by afirst solenoid, and the valve is held from opening by a second solenoid.When the second solenoid releases the valve, a ½ oscillation between thedisabler spring and valve spring opens the valve and a third solenoidholds the valve open. The first solenoid then releases the disablerspring. When the third solenoid releases the valve spring, a ½oscillation of the two springs closes the valve with a soft landing andthe second solenoid again holds the valve closed. The valve operation isvery fast, independent of engine speed, and can be controlled over 270crankshaft degrees. The solenoids, used for holding only, are very smalland require little power. The camshaft runs at crankshaft speed. Bydisabling the cylinders during compression and expansion strokes, 4stroke operation is used for gasoline motor operation. 2 strokeoperation is used for compressor and air motor operation as a pneumatichybrid.”

D. Moyer, Engine Valve Disabler, U.S. Pat. No. 6,260,525, 17 Jul. 2001,describes “A method for improving efficiency and reducing emissions ofan internal combustion engine. Variable displacement engine capabilitiesare achieved by disabling engine valves during load changes and constantload operations. Active cylinders may be operated at minimum BSFC byintermittently disabling other cylinders to provide the desired nettorque. Disabling is begun by early closing of the intake valve toprovide a vacuum at BDC which will result in no net gas flow across thepiston rings, and minimum loss of compression energy in the disabledcylinder; this saving in engine friction losses is significant withmultiple disablements.”

D. Moyer, Fuel Efficient Valve Control, U.S. Pat. No. 5,975,052, 2 Nov.1999, describes “A method for improving efficiency and reducingemissions of an internal combustion engine. Variable displacement enginecapabilities are achieved by disabling engine valves during load changesand constant load operations. Active cylinders may be operated atminimum BSFC by intermittently disabling other cylinders to provide thedesired net torque. Disabling is begun by early closing of the intakevalve to provide a vacuum at BDC which will result in no net gas flowacross the piston rings, and minimum loss of compression energy in thedisabled cylinder; this saving in engine friction losses is significantwith multiple disablements.

E. Lohse and U. Muller, Electromagnetic Actuator for a Cylinder ValveIncluding an Integrated Valve Lash Adjuster, U.S. Pat. No. 6,047,673, 11Apr. 2000, describe “An electromagnetic actuator for operating an enginevalve of an internal-combustion engine includes two electromagnets; anarmature movably disposed in the space between the electromagnets forreciprocation in response to electromagnetic forces generated by theelectromagnets; resetting springs operatively coupled to the armaturefor opposing armature motions effected by the electromagnetic forces; apush rod affixed to the armature for moving therewith as a unit; and aguide for guiding the push rod. The guide includes a guide cylinder anda push-rod piston carried by an end of the push rod. The push-rod pistonis slidably received in the guide cylinder. A setting piston is slidablyreceived in the guide cylinder and defines, with the push-rod piston, anintermediate chamber forming part of the cylinder. The setting pistonhas an end adapted to be operatively coupled to the engine valve. Afluid supply introduces hydraulic fluid into the intermediate chamber.Further, a fluid-control valve is provided which has an open state inwhich the intermediate chamber communicates with the fluid supply and aclosed state in which hydraulic fluid is locked in the intermediatechamber for rigidly transmitting motions of the push-rod piston to thesetting piston.

M. Theobald, B. Lequesne, and R. Henry, Control of Engine Load viaElectromagnetic Valve Actuators, Paper No. 940816, InternationalCongress & Exposition, Detroit, Mich., February 28-Mar. 3, 1994,describes a single-cylinder research engine equipped with programmablevalve actuators. The actuators include a permanent magnet “thateliminates the need for a holding current while the valve is fully openor closed.

F. Pischinger and P. Kreuter, Electromagnetically Operating Actuator,U.S. Pat. No. 4,455,543, 19 Jun. 1984, describe “An electromagneticallyoperating actuator for control elements capable of making oscillatorymovements in displacement machines, more particularly for flat slideshut-off valves and lift valves, includes a spring system and a pair ofelectrically operating switching elements, over which the controlelement is moveable in two discrete opposite operating positions and isretained thereat by either switching magnet, the locus of the positionof equilibrium of the spring system lying between the two operatingpositions. The invention is characterized by the provision of acompression device in engagement with the spring system for relocatingthe locus of the position of equilibrium of the spring system uponactuation of the compression device.”

D. Bonvallet, Variable Lift Electromagnetic Valve Actuator System, U.S.Pat. No. 4,777,915, 18 Oct. 1988, describes a “housing on the cylinderhead of an engine operatively supports an upper solenoid and a tubularlower solenoid such that therein working pole faces are opposed to eachother for operatively effecting movement of an armature fixed to thefree stem end of a poppet valve having its stem extending up through thelower solenoid. Upper and lower springs each have one end thereofpositioned in the upper and lower solenoids, respectively, and the lowersolenoid has an actuator operatively connected thereto to effect axialposition of the lower solenoid, while the upper solenoid has a lashadjuster operatively associated therewith.”

P. Pusic, Electrically Operated Cylinder Valve, U.S. Pat. No. 5,074,259,24 Dec. 1991, describes an “electrically operated cylinder valve and avalve operating device for an internal combustion engine”, in which thevalve is “operated by electromagnetic means energized by electricalcurrents which are controlled by electronic means. The flow of currentsdetermines the valve timing, duration, and lift according torequirements for optimal engine performance under different operatingconditions.”

J. Nitkiewicz, Method and Apparatus for Detecting Engine Valve Motion,U.S. Pat. No. 5,769,043, 23 Jun. 1998, describes a “method of andapparatus for detecting engine valve motion are provided in an internalcombustion engine having an electromechanical or electromagnetic valveactuator with a ferrous component that moves in a linear path with thereciprocating motion of an engine valve between its open and closedpositions. The apparatus includes a stationary magnetic field sourcemounted in the actuator and having an axis aligned with the linear pathand positioned such that, at its closest position of travel, the ferrouscomponent alters the magnetic field flux of the magnetic field source. Asensor mounted in the longitudinal path between the stationary magneticfield source and the ferrous component and sufficiently spaced from themagnetic field source responds to an amplified change in magnetic fieldflux at its closest travel position, sensing the change in the magneticfield flux of the stationary magnetic field source caused by thepresence and absence of the ferrous component in the closest travelposition as an indicator of engine valve motion.”

F. Schlomi, J. Rogozinski, V. Ivanov, and U. Arkashevski, Solenoid Valvewith Permanent Magnet, U.S. Pat. No. 6,199,587, 13 Mar. 2001, describe asolenoid valve which “comprises a first coil, a plunger, a first and asecond opening in the valve, and a latching mechanism placed inassociation with the first opening. The latching mechanism causeslatching, with a predetermined latching force, of the plunger to thefirst opening, and energization of the first coil along a predeterminedfirst polarity causes at least a reduction of the latching force. Theplunger has a first end towards the first opening and a second endtowards the second opening, and a magnetic field extensor extends afirst pole of the magnetic field produced by the first coil to the firstend of the plunger. The extensor comprises a hollow cylindrical ferrousmember terminated by a ferrous endpiece and is movable, with theplunger, relative to the first opening.”

P. Kreuter and K. Schmitz, Electromagnetically Operated AdjustingDevice, U.S. Pat. No. 5,199,392, 6 Apr. 1993, describe “an actuatorassembly for an electromagnetically-actuated, spring-loaded positioningsystem in displacement engines, such as for lifting valves in internalcombustion engines. The positioning mechanism comprises a three-springsystem and two electrically-operated, opposed actuating solenoids, bymeans of which the actuator may be moved therebetween, and held at, twodiscreet, mutually-opposite operating positions. The actuator assemblyfurther comprises an anchor plate having integrally attached upper andlower stems, wherein the lower stem engages the upper flanged end of avalve stem and, upon reciprocation of the anchor plate, transfersmovement to the valve stem which moves the valve from a closed to anopen position, or vice-versa. The actuator assembly is symmetricallybiased by upper and lower halves of the three-spring system. The upperspring system includes a first spring disposed to engage the upper stemand stressed to force the actuator assembly to the open position of thevalve head. The lower spring system comprises: A second spring disposedto engage the lower stem and stressed to move the actuator assembly tothe closed position of the valve head; and A third spring disposed toengage a stamp flange on the upper end of the valve stem which spring isstressed to assist the second spring in moving the actuator assembly tothe closed position of the valve head. Spring constants of each springare selected to provide a constant neutral point of the spring systemover the service life of the actuator assembly.”

D. Maley, R. Shinogle, M. Sommars, and O. Sturman, Fuel InjectionControl Valve with Dual Solenoids, U.S. Pat. No. 5,494,219, 27 Feb.1996, describe a “control valve assembly adapted for a fuel injectorincludes a valve seat with fluid inlet and fluid outlet. A poppet valvecontrols the flow of fluid through the valve seat. A pair of electricalactuators are selectively operably energized for releasing the poppetand moving the poppet to valve open and closed positions. Split fuelinjection can be provided using either sequential operation orconcurrent operation, i.e., phasing. Permanent magnets, holding currentand residual magnetism enable the latching of the poppet valve in eachof the valve open and closed positions.”

F. Liang and C. Hammann, Electromechanically Actuated Valve withMultiple Lifts and Soft Landing, U.S. Pat. No. 5,647,311, 15 Jul. 1997,and Electromechanically Actuated Valve with Multiple Lifts, U.S. Pat.No. 5,692,463, 2 Dec. 1997, describe an “electromechanically actuatedvalve for use as an intake or exhaust valve in an internal combustionengine. The valve is actuated by a electromechanical actuator assemblywhich includes a first electromagnet, a second electromagnet and a thirdelectromagnet. A first disk is mounted to the valve in a gap between thesecond and third electromagnets, and a second disk is slidably mountedto the valve between an insert and the first electromagnet. An extensionon the second electromagnet extends to the second disk, allowing thesecond disk to move the second electromagnet relative to the thirdelectromagnet, thereby changing the gap and thus the valve lift. A firstspring, mounted between the second electromagnet and first disk, and asecond spring, mounted between the first disk and an actuator housing,create an oscillatory system which drives most of the valve movementduring engine operation, thus reducing power requirements to actuate thevalves while increasing the responsiveness of the valves.”

While other prior art valve systems which use electromagnetic force tomove a valve, there is no provision to promote eliminate or reduce ahard landing, which typically results in extremely short valve life, ina structure which retains a valve in either an open or a closedposition, within little or no added energy.

It would be advantageous to provide an electromechanical valve systemwhich is latchable with little or no applied energy in either an open ora closed position. Such a system would be a major technologicalbreakthrough. Furthermore, it would be advantageous to provide anelectromechanical valve system which allows a soft landing at either endof movement. Such a system would be a further technologicalbreakthrough. As well, it would be advantageous to provide anelectromechanical valve system which is readily controllable to increaseor decrease the local magnetic flux, such as to promote movement of thevalve, or to provide a soft landing of the valve at either end ofmovement. In addition, it would be advantageous to provide anelectromechanical valve system which provides energy recovery, feedback, and/or feed forward sensing and control. Such a system would be afurther technological breakthrough.

SUMMARY OF THE INVENTION

Systems are provided for electromagnetic actuation of a valve mechanism.A valve is linearly moveable between a first closed position and asecond open position. A first spring is compressed when the valve is inthe first closed position, and a second valve spring is compressed whenthe valve is in the second open position. An electromagnetic actuationassembly and a permanent magnet is combined with the valve, such thatthe valve is latchable in either a closed or open position, and isreadily movable between positions through application of energy to theelectromagnetic circuitry. The electromagnetic circuitry is controllableto increase or decrease the local magnetic flux, such as to promotemovement of the valve, or to provide a soft landing of the valve ateither end of movement. Some system embodiments provide energy recovery,feed back, and/or feed forward sensing and control. The electromagneticvalve system can be implemented for a wide variety of engines, valvesand actuators, such as for variable valve timing, valve disablement,and/or hybrid engine and energy storage applications.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a partial cross sectional view of an electromagnetic valvesystem;

FIG. 2 is a top schematic view of a permanent magnet clapper;

FIG. 3 is a partial cutaway view of a Model 1 single solenoid magneticvalve control system;

FIG. 4 is a chart showing material characteristics for a permanentmagnet;

FIG. 5 is a chart which shows magnetic induction as a function ofmagnetic field intensity for core material;

FIG. 6 is a chart which shows magnetic force of the permanent magnet asa function of displacement variation for a single solenoid magneticvalve control system;

FIG. 7 is a chart which shows incremental inductance as a function ofcurrent for a given air gap for a single solenoid magnetic valve controlsystem;

FIG. 8 is a chart which shows incremental magnetic force as a functionof current for a given air gap for a single solenoid magnetic valvecontrol system;

FIG. 9 is a transient analysis chart which shows displacement as afunction of time for an applied voltage of 12 volts, with no eddycurrent;

FIG. 10 is a transient analysis chart which shows current as a functionof time for an applied voltage of 12 volts, with no eddy current;

FIG. 11 is a transient analysis chart which shows displacement as afunction of time for an applied voltage of 24 volts, with no eddycurrent;

FIG. 12 is a transient analysis chart which shows current as a functionof time for an applied voltage of 24 volts, with no eddy current;

FIG. 13 is a transient analysis chart which shows displacement as afunction of time for an applied voltage of 12 volts, with eddy currenteffects;

FIG. 14 is a transient analysis chart which shows current as a functionof time for an applied voltage of 12 volts, with eddy current effects;

FIG. 15 is a transient analysis chart which shows displacement as afunction of time for an applied voltage of 24 volts, with eddy currenteffects;

FIG. 16 is a transient analysis chart which shows current as a functionof time for an applied voltage of 24 volts, with eddy current effects;

FIG. 17 is a partial cutaway view of a Model 2 double solenoid,three-leg magnetic valve control system;

FIG. 18 is a chart which shows magnetic force of the permanent magnet asa function of displacement variation for a double solenoid, three-legmagnetic valve control system;

FIG. 19 is a chart which shows incremental inductance as a function ofcurrent for a given air gap for a double solenoid three leg magneticvalve control system;

FIG. 20 is a chart which shows incremental magnetic force as a functionof current for a given air gap for a double three-leg solenoid magneticvalve control system;

FIG. 21 is a transient analysis chart which shows displacement as afunction of time for an applied voltage of 12 volts, including eddycurrent, for a double solenoid three-leg magnetic valve control system;

FIG. 22 is a transient analysis chart which shows current as a functionof time for an applied voltage of 12 volts, including eddy current, fora double solenoid three-leg magnetic valve control system;

FIG. 23 is a transient analysis chart which shows displacement as afunction of time for an applied voltage of 24 volts, including eddycurrent, for a double solenoid three-leg magnetic valve control system;

FIG. 24 is a transient analysis chart which shows current as a functionof time for an applied voltage of 24 volts, including eddy current, fora double solenoid three-leg magnetic valve control system;

FIG. 25 is a partial cutaway view of a Model 3 double solenoid, threeleg flux return path magnetic valve control system;

FIG. 26 is a chart which shows magnetic force of the permanent magnet asa function of displacement variation for a double solenoid, three-legflux return path magnetic valve control system;

FIG. 27 is a chart which shows incremental inductance as a function ofcurrent for a given air gap for a double solenoid three leg flux returnpath magnetic valve control system;

FIG. 28 is a chart which shows incremental magnetic force as a functionof current for a given air gap for a double three-leg flux return pathsolenoid magnetic valve control system;

FIG. 29 is a schematic cross sectional view showing equi-potentialmagnetic force lines for a Model II double three leg flux solenoidmagnetic valve control system without current;

FIG. 30 is a schematic cross sectional view showing equi-potentialmagnetic force lines for a Model III double three leg flux solenoidreturn path magnetic valve control system without current;

FIG. 31 is a schematic cross sectional view showing equi-potentialmagnetic force lines for a Model II double three leg flux solenoidmagnetic valve control system with an applied current;

FIG. 32 is a schematic cross sectional view showing equi-potentialmagnetic force lines for a Model III double three leg flux solenoidreturn path magnetic valve control system with an applied current;

FIG. 33 is a first cutaway view of an electromagnetic valve actuationsystem comprising discrete spring and electromagnet assemblies;

FIG. 34 is a second cutaway view of an electromagnetic valve actuationsystem comprising discrete spring and electromagnet assemblies;

FIG. 35 is a top schematic view of an electromagnetic valve actuationsystem comprising discrete spring and electromagnet assemblies;

FIG. 36 is a first cutaway view of a preferred electromagnetic valveactuation system comprising discrete spring and electromagnetassemblies;

FIG. 37 is a second cutaway view of a preferred electromagnetic valveactuation system comprising discrete spring and electromagnetassemblies;

FIG. 38 is a schematic view of an electromagnetic valve system having areciprocating disk clapper comprised of a ferrous or magnetic material;

FIG. 39 is a schematic view of an electromagnetic valve system whichcomprises a permanent magnet reciprocating disk clapper;

FIG. 40 is a schematic view of a controller and power module linked toan electromagnetic valve system;

FIG. 41 is a detailed schematic view of control and power circuitryassociated with an electromagnetic valve system;

FIG. 42 is a schematic diagram of generic structures and functionalitythroughout different embodiments of electromagnetic valve systems;

FIG. 43 is a cutaway view of an electromagnetic valve actuation systemcomprising discrete spring and electromagnet assemblies, with the valvein a closed position;

FIG. 44 is a top schematic view of an electromagnetic valve actuationsystem comprising discrete spring and electromagnet assemblies;

FIG. 45 is a detailed cross-sectional view of a mechanical springdisabler mechanism;

FIG. 46 is a detailed partial cross-sectional view of a mechanical valvedisabler system in a first position with a disabler set;

FIG. 47 is a detailed partial cross-sectional view of a mechanical valvedisabler system in a second disabled position with a disabler set;

FIG. 48 is a detailed partial cross-sectional view of a mechanical valvedisabler system in a first enabled and closed position;

FIG. 49 is a detailed partial cross-sectional view of a mechanical valvedisabler system in a second enabled and opened position;

FIG. 50 is a detailed partial cross-sectional view of an alternatemechanical valve disabler system in a first position with a disablerset;

FIG. 51 is a detailed partial cross-sectional view of an alternatemechanical valve disabler system in a second disabled position with adisabler set;

FIG. 52 is a detailed partial cross-sectional view of an alternatemechanical valve disabler system in a first enabled and closed position;

FIG. 53 is a detailed partial cross-sectional view of an alternatemechanical valve disabler system in a second enabled and openedposition;

FIG. 54 is a partial detailed cutaway view of a spring latch mechanism;and

FIG. 55 is a profile view of a reverse profile cam lobe.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

FIG. 1 is a partial cross sectional view of an electromagnetic valvesystem 10 a. A valve 12, having a stem 14, is linearly moveable within acylinder head 16, such as through a valve guide 18. The valve 12 islinearly moveable between a closed position 20 a and an open position 20b, to allow flow into or out of a manifold port 22.

The valve 12 comprises a valve face 24 at one end of the stem 14. Aclapper 26 is affixed to the stem 14, such that movement of the clapperresults in movement of the valve 12. A valve spring 28 is locatedbetween the head 16 and the clapper 26, which biases the valve 12 towarda closed position 20 a. A disable spring 30 is located on an opposingsurface of the clapper 26, to bias the valve 12 toward an open position20 b. The disable spring 30 is typically affixed in relation to thecylinder head 16, such as by a retainer 32.

A first permanent magnet 34 a and first electromagnet 36 a are locatedon one side of the clapper 26, and a second permanent magnet 34 b andfirst electromagnet 36 b are located on the opposing side of the clapper26. In a closed position 20 a, the magnetic flux of the second permanentmagnet 34 b provides an attractive magnetic force to retain the clapper26, such as to latch the valve 12 in the closed position 20 a.Similarly, in an open position 20 b, the magnetic flux of the secondpermanent magnet 34 a provides an attractive magnetic force to retainthe clapper 26, such as to latch the valve 12 in the open position 20 b.

The electromagnetic coils 36 a,36 b typically comprise a toroidal core56 (FIG. 3), around which electrically conductive wire 54 is wound.Electrical current 57 (FIG. 3) is controllably applied in eitherdirection, such as through the wire 54, such that the electromagneticcoils 36 a,36 b are operable to provide a magnetic flux in eithervertical direction.

In operation, the electromagnetic valve system 10 a is readily moveablebetween positions 20 a,20 b. Applied energy to the electromagnets 36acts to increase or decrease the total magnetic attraction of theclapper 26.

From a closed position 20 a, applied energy to the secondelectromagnetic coil 36 b provides a magnetic flux in a generallyopposite direction to the magnetic flux from the second permanent magnet34. In the closed position 20 a, the disable spring 30 comprises storedpotential energy. When the total magnetic force 82 (FIG. 6) becomes lessthan the force from the potential energy of the compressed disablespring 30, the clapper 26 and valve 12 move linearly downward toward theopen position. As the clapper contacts the valve spring 28, the valvespring 28 is compressed. As the valve approaches the open position 20 b,the magnetic flux of the first permanent magnet 34 provides anattractive magnetic flux. The first electromagnetic coil 34 a maypreferably be energized as the valve approaches the open position 20 b,such as to increase the attractive, i.e. pulling, magnetic force 82.

In addition, the first electromagnetic coil 36 a may preferably beenergized near the end of travel, as the valve 12 approaches the openposition 20 b, such as to slow the advance of the clapper 26, andprovide a soft landing in the open position 20 b. The magnetic fluxprovided by some permanent magnets 34 increases significantly at shortdistances, such as to increase the attractive, i.e. pulling, magneticforce 82. Activation of the electromagnetic coil 36 a to provide a softlanding typically comprises a short time period, such as a pulse, toslow the approach of the clapper 26.

Similarly, from an open position 20 b, applied energy to the firstelectromagnetic coil 36 a provides a magnetic flux in a generallyopposite direction to the magnetic flux from the first permanent magnet34 a. In the open position 20 b, the valve spring 28 comprises storedpotential energy. When the total magnetic force 82 becomes less than thepotential energy, the clapper 26 and valve 12 move linearly upwardtoward the closed position 20 a. As the clapper 26 contacts the disablespring 30, the disable spring 30 is compressed. As the valve 12approaches the closed position 20 a, the magnetic flux of the secondpermanent magnet 34 b provides an attractive magnetic flux. The secondelectromagnetic coil 36 b may preferably be energized as the valve 12approaches the closed position 20 a, such as to increase the attractive,i.e. pulling, magnetic force 82.

In addition, the second electromagnetic coil 36 b may preferably beenergized near the end of travel, as the valve 12 approaches the closedposition 20 a, such as to slow the advance of the clapper 26, andprovide a soft landing in the closed position 20 a Activation of theelectromagnetic coil 36 a to provide a soft landing typically comprisesa short time period, such as a pulse, to slow the approach of theclapper 26.

In some embodiments of the electromagnetic valve system 10, the clappercomprises one or more permanent magnets 42. In alternate embodiments ofthe electromagnetic valve system 10, the clapper comprises magneticallyattractive, i.e. ferrous material.

FIG. 2 shows a partial detailed top view of a clapper 26 comprising aplurality of radially aligned permanent magnets 42. As seen in FIG. 2,each of the magnets 42 is radially aligned toward the valve stem 14,wherein the north poles 44 face inward, and wherein the south poles 46face outward.

FIG. 3 is a partial cutaway view of a Model 1 single solenoid magneticvalve control system 10 b, in which a permanent magnet clapper 26 a isaffixed to the stem 14 of a valve, and is moveable between a firstelectromagnet 36 a and a second electromagnet 36 b. The electromagneticcoils 36 a,36 b are located within yoke assemblies 52 a,52 b, andcomprise wire coils 54 on a core 56. The clapper 26 comprises a magneticregion 42 within a clapper yoke 58.

FIG. 4 is a chart 60 showing material demagnetization characteristiccurves 66,68 for a permanent magnet 42, comprised of Sm₂Co₁₇, as afunction of magnetic field 64 at various temperatures.

FIG. 5 is a chart 70 which shows 76 magnetic induction 72 as a functionof magnetic field intensity 74 for core material, comprised of steel,having a density of 7.9 g/cm3, and an electrical conductivity of 1.03e7(1/ohm·m).

FIG. 6 is a chart 80 which shows 86 magnetic force 82 of the permanentmagnet 42 as a function of displacement variation 84 for a singlesolenoid magnetic valve control system 10. As seen in FIG. 6, at closeseparation distances 88, the magnetic attraction force increasessignificantly. For example, at a separation distance of 0.03 mm, theattractive force of a Type One clapper 26 provides 416 N of attractiveforce.

FIG. 21 is a chart showing material characteristics for a permanentmagnet material used in some embodiments of the clapper 26, for a magnetcomprising SmsCo17, having a density of 7.5 g/cm3, a conductivity of1.16e6 (1/ø·m), and a rated operating temperature of 150 degrees C.

FIG. 22 is a chart which shows magnetic induction as a function ofmagnetic field intensity for core material, for a steel density of 7.9g/cm3, and an electrical conductivity of 1.03e7 (1/ø·m)

In some embodiments of the invention, the winding comprises 24 AWGcopper wire, having a bare diameter of 0.511 mm, and a conductivity of5.8e7 (1/ø·m). The valve stem 14 comprises non-metallic material, andcomprised a total mass of 80 gm, and the spring constant for the firstspring 39 and for the second spring 30 is 30600 N/m.

FIG. 7 is a chart 90 which shows 96 incremental inductance 92 as afunction of current 94 for an air gap of 30 μm in a single solenoidmagnetic valve control system 10 x. FIG. 8 is a chart 100 which shows106 incremental magnetic force 82 as a function of current 94 for an airgap of 30 μm in a single solenoid magnetic valve control system 10 x.

FIG. 9 is a transient analysis chart 110 which shows 114 displacement 84as a function of time 112 for an applied voltage of 12 volts, with noeddy current, for a time period of 16.5 msec. FIG. 10 is a transientanalysis chart 120 which shows 124 current 94 as a function of time 112for an applied voltage of 12 volts, with no eddy current.

Considering Conductivity (Including Eddy Current). FIG. 11 is atransient analysis chart 130 which shows 134 displacement 84 as afunction of time 112 for an applied voltage of 24 volts, with no eddycurrent. FIG. 12 is a transient analysis chart 140 which shows 144current 94 as a function of time 112 for an applied voltage of 24 volts,with no eddy current.

FIG. 13 is a transient analysis chart 150 which shows 154 displacement84 as a function of time 112 for an applied voltage of 12 volts, witheddy current effects, in which there is no latching achieved between aclapper 26 and an electromagnet assembly 36. FIG. 14 is a transientanalysis chart 160 which shows 164 current 94 as a function of time 112for an applied voltage of 12 volts, with eddy current effects.

FIG. 15 is a transient analysis chart 170 which shows 174 displacement84 as a function of time 112 for an applied voltage of 24 volts, witheddy current effects. FIG. 16 is a transient analysis chart 180 whichshows 184 current 94 as a function of time 112 for an applied voltage of24 volts, with eddy current effects.

Model 3 System Details. FIG. 17 is a partial cutaway view 190 of a Model2 double solenoid, three leg magnetic valve control system 10 c, inwhich a permanent magnet clapper 26 a is affixed to the stem 14 of avalve 12, and is moveable between a first electromagnet 34 a and asecond electromagnet 34 b. The electromagnetic coils 36 a,36 b arelocated within yoke assemblies 52 a,52 b, and comprise wire coils 54 ona core 56. The clapper 26 comprises aligned magnetic regions 42 a,42 bwithin a clapper yoke 58.

FIG. 18 is a chart 200 which shows 204 magnetic force 82 of thepermanent magnet as a function of displacement 84 variation for a doublesolenoid, three leg magnetic valve control system 10 c.

FIG. 19 is a chart 210 which shows incremental inductance 92, comprisingindividual coil inductance 214 a,214 b and combined mutual inductance216, as a function of current 94 for a given air gap for a doublesolenoid three leg magnetic valve control system 10 c.

FIG. 20 is a chart 220 which shows 224 incremental magnetic force 82 asa function of current 94 for a given air gap for a double three legsolenoid magnetic valve control system 10 c.

FIG. 21 is a transient analysis chart 230 which shows 234 displacement84 as a function of time 112 for an applied voltage of 12 volts,including eddy current, for a double solenoid three leg magnetic valvecontrol system 10 c. FIG. 22 is a transient analysis chart 240 whichshows 244 current 94 as a function of time 112 for an applied voltage of12 volts, including eddy current, for a double solenoid three legmagnetic valve control system 10 c.

FIG. 23 is a transient analysis chart 250 which shows 254 displacement84 as a function of time 112 for an applied voltage of 24 volts,including eddy current, for a double solenoid three leg magnetic valvecontrol system 10 c. FIG. 24 is a transient analysis chart 260 whichshows 264 a,264 b current 94 as a function of time for an appliedvoltage of 24 volts, including eddy current, for a double solenoid threeleg magnetic valve control system 10 c.

Flux Return Path Embodiments. FIG. 25 is a partial cutaway view 270 of aModel 3 double solenoid, three leg flux return path magnetic valvecontrol system 10 d, in which a permanent magnet clapper 26 a is affixedto the stem 14 of a valve 12, and is moveable between a firstelectromagnet 34 a and a second electromagnet 34 b. The electromagneticcoils 34 a,34 b are located within yoke assemblies 52 a,52 b, andcomprise wire coils 54 on a core 56. The clapper 26 comprises magneticregion 42 a,42 b within a clapper yoke 58.

FIG. 26 is a chart 280 which shows 284 magnetic force of the permanentmagnet as a function of displacement variation for a double solenoid,three leg flux return path magnetic valve control system.

FIG. 27 is a chart which shows incremental inductance as a function ofcurrent for a given air gap for a double solenoid three leg flux returnpath magnetic valve control system.

FIG. 28 is a chart which shows incremental magnetic force as a functionof current for a given air gap for a double three leg flux return pathsolenoid magnetic valve control system.

Flux Fields. FIG. 29 is a schematic cross sectional view showingequi-potential magnetic force lines for a Model II double three leg fluxsolenoid magnetic valve control system without current.

FIG. 30 is a schematic cross sectional view showing equi-potentialmagnetic force lines for a Model III double three leg flux solenoidreturn path magnetic valve control system without current.

FIG. 31 is a schematic cross sectional view showing equi-potentialmagnetic force lines for a Model II double three leg flux solenoidmagnetic valve control system with an applied current.

FIG. 32 is a schematic cross sectional view showing equi-potentialmagnetic force lines for a Model III double three leg flux solenoidreturn path magnetic valve control system with an applied current.

FIG. 33 is a first cutaway view 190 of an electromagnetic valveactuation system 10 e comprising discrete spring and electromagnetassemblies, with the valve 12 in a closed position 20 a. FIG. 34 is asecond cutaway view 200 of an electromagnetic valve actuation system 10e comprising discrete spring and electromagnet assemblies, with thevalve 12 in an open position 20 b. FIG. 35 is a top schematic view 206of an electromagnetic valve actuation system 10 e comprising discretespring and electromagnet assemblies 198 a, 198 b.

A spring keeper 192 affixed to the valve stem 14 moves linearly totransfer energy between the disable spring 30 and the valve spring 28. Aclapper 26 affixed to the valve stem 14 moves between an upper magnetassembly 198 b and a lower magnet assembly 198 a. The upper magnetassembly 198 b comprises an upper permanent magnet 34 b and an upperelectromagnet 36 b, while the lower magnet assembly comprises a lowerpermanent magnet 34 a and a lower electromagnet 36 a.

As seen in FIG. 33 and FIG. 34. the springs 28,30 are preferablyfastened the far bearing ends, and are not fastened to the spring keeper192, such that the springs 28,30 are preferably isolated from thedynamic mass of the valve system 10 e during a portion of the valvemovement. In one exemplary embodiment, the springs 28,30 are rated at660 lbs./per inch. In the electromagnetic valve system 10 e, the valvestem shaft is non-magnetic. The clapper 26 shown in FIG. 33 and FIG. 34also comprises a mechanical sleeve 195, such as to accurately affix theclapper 26 to the valve stem 14.

The permanent magnets 34 a,34 b provide a latching means for the clapper25, in either the closed position 20 a or the open position 20 b. Asseen in FIG. 34, the permanent magnet 34 a holds the valve spring 28compressed in the valve open position 20 b, whereby the valve spring 28retains a high level of potential energy. Similarly, as seen in FIG. 33,the permanent magnet 34 b holds the disable spring 30 compressed in thevalve closed position 20 a, whereby the disable spring 30 retains a highlevel of potential energy.

From the closed position 20 a, wherein the clapper 26 is latched againstthe upper magnet assembly 198 b, an applied energy to the upperelectromagnet 36 b is controllably energized to release the clapper fromthe closed position 20 a. Upon activation of energy to the firstelectromagnet 36 b, an electromagnetic flux is generated by theelectromagnet 36 b, which opposes the permanent magnet flux of the upperpermanent magnet 34 b. When the applied opposing electromagnetic fluxreduces the permanent magnet holding force below that of the springforce applied by the disable spring 30, the valve 12 begins to open.

As the valve 12 begins to open, the applied force of the upper permanentmagnet 34 b, which has a constant flux, is reduced. As the valve 12opens and the clapper 26 moves away from the upper magnet assembly 198b, whereby the applied flux density from the permanent magnet 34 b fallsoff very rapidly, such that the attractive force decreases rapidly.

Similarly, as the valve 12 begins to close, the applied force of thelower permanent magnet 34 a, which has a constant flux, is reduced. Asthe valve 12 closes and the clapper 26 moves away from the lower magnetassembly 198 b. The applied flux density from the permanent magnet 34 afalls off very rapidly, such that the attractive force decreasesrapidly.

As the spring keeper 192 moves and advances toward the middle region193, the spring forces are equal, and the kinetic energy of the systemreaches a maximum. The spring keeper 192 continues to move, a wherebythe kinetic energy of the moving mass of the assembly 195 is convertedto stored potential energy in the valve spring 28. The moving mass ofthe assembly 195 is typically equal to the combined mass of the clapper26, the valve 12, the keeper 192, and at least a portion of the springs28,30.

In preferred embodiments of the electromagnetic actuation system 10, thekinetic mass of the valve train 195 is minimized by the configuration ofthe valve spring 28 and the disable spring 30, whereby kinetic energy istransferred between the valve spring 28 and the disable spring 30, in acentral region 193 of movement, and whereby the mass of either the firstor second spring 28,30 is substantially isolated from the effective massof valve train 195 for a portion of movement.

For example, as seen in FIG. 33 and FIG. 34, as the spring keeper 192moves beyond the central region 193, the valve spring 28 is compressedby further downward movement of the valve assembly 195, comprising theclapper 296 the valve 12, and spring keeper 192, while the disablespring 30 becomes isolated from the assembly 195 (FIG. 34).

When the valve assembly 195 approaches the end of travel, e.g. such astoward an open position 20 b, the valve 12, clapper 26, and springkeeper 192 decelerate, as the kinetic energy of the valve assembly 195is transformed to stored potential energy in the valve spring 28. Nearthe limit of travel, the applied flux from the lower permanent magnet 34a provides an attractive force to latch the valve 12 in the openposition 20 b.

As described above, the attractive force from between the permanentmagnets 34 and the electromagnets 36 is proportional to the displacementdistance 84, i.e. there is a strong attractive force at the very endregion of travel. In preferred embodiments of the invention, therefore,energy may be controllably applied to the approaching electromagnet 36,to promote a ‘soft’ landing.

When the spring keeper 192 compresses the valve spring 28 to the bottomlimit of movement, i.e. wherein the clapper 26 approaches the bottommagnet assembly 198 a, the clapper 26 contacts and latches to the lowermagnet assembly 198 a, since the magnet force 82 increases as theclapper 26 approaches the magnet assembly 198 a. At the limit of travel,the magnetic holding force is larger than the opposing valve springforce, such that the valve 12 latches in the open position 20 b.

In the electromagnetic valve system 10 e shown in FIG. 33 and FIG. 34,the valve 12 latches in either the closed position 20 a or in the openposition 20 b, without the application of energy.

Release from either latch condition is controllable through appliedenergy signal, such as from an external control 302 (FIG. 40, FIG. 41).As seen in FIG. 41, an external controller 302 sends a signal, i.e.energy pulse, to the appropriate magnet assembly 198, which is latchedto the clapper 26. The applied pulse overcomes the permanent magnetattraction force, such that the compressed spring, e.g. the valve spring28, acts upon the assembly 195, which moves toward the oppositeposition.

FIG. 36 is a first cutaway view 210 of a preferred electromagnetic valveactuation system 10 f comprising discrete spring 224 and electromagnet226 assemblies, in a closed position 20 a. FIG. 37 is a second cutawayview of a preferred electromagnetic valve actuation system 10 fcomprising discrete spring 224 and electromagnet 226 assemblies, in anopen position 20 b. The electromagnetic valve actuation system 10 fcomprises a single axially polarized, single, non-moving permanentmagnet 34, and a single electromagnet and coil 36.

The spring assembly 224 comprises two separate springs 28,30, which actindependently, i.e. the springs 28,30 are alternately isolated from thedynamic mass of the valve assembly 195, which reduces the spring movingmass, and reduces spring friction.

The permanent magnet 34 is preferably square or rectangular, in verticalcross section, to provide an increased magnetic flux over the footprintof the cylinder head 16. The square or rectangular permanent magnet 34has more flux than a round one of equal diameter, which allows springs28,30 having higher spring forces to be used.

The electromagnetic valve actuation system 10 f also preferablycomprises full width magnet poles 212,214, to carry more magnetic flux.The clapper 26 is typically cylindrical in profile, to allow rotation ofthe valve 12.

In the exemplary embodiment shown in FIG. 36 and FIG. 37, the valve stem14 screws into the clapper 26, and is preferably held with a lockingcompound 227, such as LOCTITE™, such that the spring keeper 192 ismechanically affixed to the valve assembly 195. In some systemembodiments, the spring keeper 192 acts as a piston, to balance themanifold pressure.

In some system embodiments, the fixed ends 228 of the springs 28,30 arescrewed into position, to retain the springs in a perpendicularposition, with the vertical forces equally distributed across thesprings 28,30. The valve seat and the opening stop 222 stops the keeper192 near seating, to provide adjustment for temperature and wear.

The free lengths of the springs 28,30 preferably overlap slightly, sothat the moving spring mass 195 can transfer kinetic energy at the midpoint 193 (FIG. 34).

System Operation. As seen in FIG. 36, the valve 12 is shown in theclosed position 20 a. To open the valve 12, the coil 36 is energized tooppose the permanent magnet flux (PMF) and effectively cancel the PMFholding force, which causes the disabler spring 30 force to acceleratethe valve 12 in the opening direction 20 b.

As the valve 12 moves away from the magnet pole, the PMF decreases, andthe opening 12 flux is proportionately decreased, so as to minimize themagnetic force. When the keeper 192 approaches the midpoint 193, thekeeper 192 contacts the valve spring 28. The disabler spring 30 deliverskinetic energy to the valve spring 28, by the time the disabler spring30 reaches a free length, where the disable spring 30 stops moving. Thevalve spring 28 absorbs the kinetic energy, and decelerates the movingmass 195 toward the open position 20 b.

During the valve motion, friction and windage typically absorb a smallportion of the kinetic energy, which slows the valve motion. When thekeeper 192 passes the mid-point 193, the coil 36 is energized in theopposite direction, to assist the PMF of the permanent magnet 34, and tomake up the kinetic energy lost to friction and windage. The assistingflux from the coil 36 is typically proportionately decreased, so thatthe keeper 192 arrives at the stop 222 with close to zero speed, and themagnetic force PMF from the permanent magnet 34 holds the valve 12 open20 b.

The controlled movement of the valve system 10 f from the open position20 b to the closed position 20 a is provided by the reverse of theopening motion. To close the valve 12, the coil 36 is energized tooppose the permanent magnet flux (PMF) and effectively cancel the PMFholding force, which causes the valve spring 28 force to accelerate thevalve 12 in the closing direction 20 a.

Similarly, as the valve 12 moves away from the magnet pole, the PMFdecreases, and the opening 12 flux is proportionately decreased, so asto minimize the magnetic force. When the keeper 192 approaches themidpoint 193, the keeper 192 contacts the disable spring 30. The valvespring 28 delivers kinetic energy to the disable spring 30, by the timethe valve spring 28 reaches a free length, where the valve spring 28stops moving. The disable spring 30 absorbs the kinetic energy, anddecelerates the moving mass 195 toward the closed position 20 a. Aswell, the assisting flux from the coil 36 is typically proportionatelydecreased, so that the keeper 192 arrives at the top position with closeto zero speed, and the magnetic force PMF from the permanent magnet 34holds the valve 12 closed 20 a.

FIG. 38 is a schematic view 240 of an electromagnetic valve system 10 ghaving a clapper 26 comprised of a ferrous or magnetic material, whereinthe clapper 26 comprises a reciprocating disk. In some systemembodiments, the permanent magnets 34 are integrated within theelectromagnets 36, which provides magnetic attraction to the disk 26without the need for electrical energy.

A “reverse” electrical pulse to the appropriate electromagnet 36, e.g.36 a, cancels the permanent magnet field to cause the release of thedisk 26. The springs 28, 30 then force the disk 26 and connected valve12 to the opposing permanent/electromagnet 34,36. The disk 26 isattracted to the opposing permanent/electromagnet, where it comes torest.

The electromagnetic valve system 10 h provides latching, either open orclosed, without requiring power, even after the engine is turned off.Only a brief current pulse is required to cause the valve 12 to switchto the opposing position 20 a,20 b. Thus, power is only consumed for abrief period. As the permanent magnet clapper 26 approaches theelectromagnet 36, the changing magnetic field is preferably converted toelectrical energy, to be returned to a power module 304 (FIG. 40, FIG.41). In some embodiments, the electromagnets 36 a,36 b additionallyrepel the clapper 26, such as to provide for fast valve speeds.

FIG. 39 is a schematic view of an electromagnetic valve system 10 hwhich comprises a permanent magnet clapper 26, wherein the clapper 26comprises a permanent magnet reciprocating disk. The reciprocating diskclapper 26 is attached to the engine valve 12, such as by a rod thatpasses through one electromagnet 36. Electromagnets 36 a,36 b are placedat both ends of the disk travel. The electromagnets 36 have the abilityto controllably attract or repel the permanent magnet clapper 26,depending on the polarity of the voltage applied to the electromagnet36. When the permanent magnet 36 in not in close proximity to theelectromagnet (within approximately 0.05 inches), the only forces actingon the magnet clapper are spring forces. The two springs 28,30accelerate and decelerate the disk 26 and valve 12 to the opposing valvepositions 20 a,20 b.

The electromagnetic valve system 10 h provides latching, either open orclosed, without requiring power, even after the engine is turned off.Only a brief current pulse is required to cause the valve 12 to switchto the opposing position 20 a,20 b. Thus, power is only consumed for abrief period. As the permanent magnet clapper 26 approaches theelectromagnet 36, the changing magnetic field is preferably converted toelectrical energy, to be returned to an energy exchange and storagesystem (FIG. 41), e.g. such as a battery or an LC circuit. In someembodiments, the electromagnets 36 a,36 b additionally repel thepermanent magnet clapper 26, such as to provide for fast valve speeds.

The electromagnetic valve system 10 h is typically comprises low eddycurrent, i.e. low loss, materials as well as energy recovery circuitry,will help reduce energy consumption. Some embodiments of theelectromagnetic valve system 10 h provide soft landing controls, suchthat the valve 12 and/or disk 26 do not “slam” into other engine partsas the valve comes to rest. The soft landing control typically comprisesthe provision of a short electrical repelling force to the appropriateelectromagnet 36, as the disk 26 approaches. In some system embodiments,at least a portion of the energy required for the soft landing pulse isprovided from the energy recovery circuitry.

System Control and Power Circuitry. FIG. 40 is a schematic view 300 of acontroller 302 and power module 304 linked to an electromagnetic valvesystem 10. FIG. 41 is a detailed schematic view 350 of control 302 andpower circuitry 304 associated with an electromagnetic valve system 10.While the exemplary system 10 is similar in detail to system 10 e, asseen in FIG. 33 and FIG. 34, the controller 302 and power module 304 arereadily used throughout the various system embodiments 10.

System Advantages. The electromagnetic valve systems 10 can be used fora wide variety of applications. The electromagnetic valve system 10 isable to controllably open and or close a valve 12 at any time, and isnot mechanically limited to camshaft and/or a crankshaft.

The opening and/or closing of valves 12 is readily accomplished at anytime within an engine cycle. Furthermore, one or more valves 12 arereadily latched in either an open or a closed position, such that one ormore cylinders may readily be disabled.

In applications for an internal combustion engine, valve timing andduration is readily controlled and modified. For example, in some engineapplications, the electromagnetic valve system provides real-timeprofiling of valve operation, such as to provide longer valve duration,to alter valve timing for opening and/or closing.

Valve trains in conventional engines are linked through a camshaft tothe crankshaft of the engine, such that operation of the valve train isinherently linked to the crankshaft speed. In contrast, theelectromagnetic valve system is inherently independent of the speed theengine.

During a steady state operation of an engine, e.g. at a constant loadand speed, the electronic valve system can readily operate in a somewhatconventional manner, whereby the opening and closing of valves issynchronized to the crankshaft speed.

In contrast to conventional valve systems, however, the electromagneticvalve system 10 is readily controlled for any different operationconditions, such as for changes in ambient temperature, pressure,humidity, and/or internal friction.

The electromagnetic valve system 10 is also readily controlled fordiffering demands for power and/or torque, demands for acceleration ordeceleration.

Furthermore, the time to open and/or close a valve 12 in a conventionalengine is mechanically linked to a cam profile. In contrast, the time toopen and/or close a valve 12 in the electromagnetic valve system 10 isindependent of the mechanical limitations of a cam. The transit time,the time to open or close a valve 12, is controllable in theelectromagnetic valve system 10, whereby a latched valve 12 is readilyreleased and moved to an opposite position 20. In some preferredembodiments of the electromechanical valve system 10, the initialrelease of a valve 12 is enhanced by a strong electromagnetic pulse, toquickly accelerate the clapper 26 from the latched position.

Therefore, the time to open or close as valve 12 is readily minimized inthe electromagnetic valve system 10, and is independent of engine speed,whereby the valve open period is readily and precisely controlled, suchthat a cylinder can be filled with an air-fuel charge more completelyand fully, which at a low engine speed in some embodiments, provides ahigher torque output, e.g. 15-20 percent, as compared to a conventionalcam-driven engine.

In the electromagnetic valve system 10, the speed at which a valve 12 isdetermined by the applied power to the latching electromagnet.Therefore, while there is an advantage to opening and/or closing a valverapidly, the applied energy is typically increased to provide a fastrelease from a latched position. In some embodiments of theelectromagnetic control system 302 (FIG. 40), a desired valve speed andenergy consumption maximum is determined, to provide sufficient valvespeed while conserving applied energy.

Soft Landing. As described above, as the valve approaches an endpoint20, such as an open position 20 b or a closed position 20 a, the appliedforces on the valve assembly 195 include the opposing force applied bythe spring 28,30, e.g. the valve spring 28, and the attractive magneticforce between the clapper 26 and the appropriate electromagnet assembly134. As seen in FIG. 6, the attractive force of a permanent magnet 34increases significantly at small distances 84, such that the valve 12readily latches to the endpoint 20 at the end of travel.

Some embodiments of the electromagnetic valve system 10 include softlanding means to prevent a hard landing of the valve assembly 195 at alatch position, whereby a small amount of energy is applied by theelectromagnet 36 to provide a controlled opposing force between thepermanent magnet 34 and the electromagnet 36 during landing. Theresultant applied flux opposes the attractive flux of the permanentmagnet 34, to provide a soft landing.

Energy Loss and Input. In the electromagnetic valve system 10, theresistance force on the landing is dependent on friction within theassembly, whereby the potential and kinetic energy of the system, fromthe compressed spring, is reduced, due to friction.

For example, in a system which has too much friction, the valve 12 maynever reach the end of the travel, in which too much kinetic energy islost, due to friction. Under such a condition, the clapper 26 may notreach and latch to the electromagnet 36 and permanent magnet 34, and theassembly oscillates, and energy dissipates due to friction, until thetwo spring forces are equal.

The electromagnetic valve system 10 therefore typically comprises meansto input energy into the assembly 10, such as to provide an opposingelectromagnetic flux to initiate movement of the valve 12 from a latchedposition, or to provide an attractive force by the appropriateelectromagnet 36 at the end of travel, to assure that the assemblylatches at the end position.

Electromagnetic Energy Input. In the electromagnetic valve system 10,the electromagnets are preferably used to initiate travel, i.e. toovercome the attractive force of the permanent magnet in a latchposition; to input energy to the valve train, such as to promote valvespeed and/or to overcome friction; to provide an attractive force tobetween the permanent magnet at the end of a travel; and/or to providean opposing force at the end of a travel, to promote a soft landing.

The applied energy to the electromagnets 36 is typically controlled bythe processor 302, and may comprise a variety of formats, such as stepsor pulses.

The controller 302 is preferably configured to modify the appliedenergy, such as to compensate for operating conditions or desiredperformance parameters 370 a-370 n, such as but not limited totemperature, friction, long-time wear characteristics, seating of thevalve, and/or cylinder pressure applied to the face of a valve.

Use of Electromagnets as Sensors. In some preferred embodiments of theelectromagnetic valve system 10, the electromagnets 36 are also used assystem sensors.

In the electromagnetic valve system 10, the clapper 26 moves in relationto the electromagnets 36. Since the permanent magnet 36 is a fluxcarrying element, relative movement of the clapper 26 in relation to theelectromagnets 34 and/or permanent magnet can be sensed by analysis ofthe flux at the electromagnets.

For example, the controller 302 detects the rate of change of flux,whereby the speed of the clapper 26 and valve 12 is indicated. Thecontroller 302 determines the location from the speed at one or morepoints, such that the controller 302 can determine the movement andresponse of the valve train through one or more strokes 20 a,20 b.

The controller 302 preferably analyzes the movement of the valve train,and can modify the applied energy, based upon the acquired information,such as to increase energy, decrease applied energy, and/or to changethe timing if applied energy, either to enhance a current operatingcondition, or to enhance a dynamic operating condition, e.g. to providea different power or torque under an acceleration condition, or toconserve fuel during deceleration. Therefore, in the electromagneticvalve system 10, the magnets are preferably used both as a drivingforce, and as a means for sensing and control.

Active Valve Train Mass. In most embodiments of the electromagneticvalve system 10, the active mass of the electromagnetic valve assemblyis equal to the combined sum of the mass of the valve 12, the mass ofthe clapper 26, and approximately half of each spring 28,30, Wherein oneside of each spring 28,30 moves, and the opposing end of each spring28,30 is affixed. For a spring 28,30 having a mass which is linearlydistributed, the estimated active mass is approximately half that of thetotal mass of each spring 28,30.

The kinetic energy of the system 10 at the midpoint of motion, i.e.wherein the potential energy stored by the springs is a minimum, isapproximately equal to ½ mv2.

While the electromagnetic valve system 10 is described as having a botha valve spring 28 and a disable spring 30, the assembly can beconsidered to be a single, dynamic compound spring, which may alsocomprise the central clapper 26, which is controllable electronically toimpart force, to take force out, and also to determine the speed atwhich the shaft is moving.

In some embodiments of the electromagnetic valve system 10, the valvetrain comprises both a valve spring 28 and a disable spring 30, whichalternately are connected or are disconnected from the dynamic valvetrain 195.

During the periodic motion of the valve train, each spring 28,30 isextended from a compressed position, to a free length position. At thefree length position, the spring is isolated of the moving mass 195 ofthe valve train 195, which reduces the dynamic mass of the valve train.In this embodiment, the springs 28,30 are fixed to the head 16 at eachend, but are not affixed to the permanent magnet.

During the periodic motion of the valve train, as the clapper approachesthe central region 193 of travel, the clapper 26 approaches and contactsthe approaching spring which is at a resting, i.e. free length,position. When the clapper contacts the oncoming spring 28,30, theclapper 26 briefly contact with both springs 28,30, whereby the kineticenergy of the system is transferred, and the valve 12 and clapper 26continue to move, while compressing the second spring 28,30, toward thesecond end 20, e.g. toward the open position 20 b.

The dynamic valve assembly 195 exchanges kinetic energy within thecentral region 193, such as through an impact, or through a smalloverlapping region, e.g. wherein the first spring is almost fullyextended, and wherein the second spring begins to be compressed.

In embodiments of the electromagnetic valve system 10 in which springs28,30 are periodically isolated from the dynamic valve train 195, thereis a reduction in the mass of the valve train 195. In addition, there isa reduction in spring friction for the system, since the springs areperiodically isolated from the motion of the valve train 195.

Geometry Considerations. In addition to improvements in dynamic valvetrain mass and response, some preferred embodiments of theelectromagnetic valve system 10, such as seen in FIG. 36 and FIG. 37,provide design freedom within an engine environment. The stationarypermanent magnets 34 can be provided in a wide variety of form factors,such as a rectangular structure, to provide a greater magnetic fluxfield than a system having axial restrictions, e.g. such as for acylindrical movable permanent magnet.

In the head of typical engine there is typically a fixed distancebetween the centerline of an exhaust valve 102 and the centerline of theintake valve 102. For a fixed separation distance, the alternateelectromagnetic valve system 10 seen in FIG. 36 and FIG. 37 providesdesign flexibility, since the stationary permanent magnets can beconfigured across the cylinder head, e.g. such as perpendicular to theline between valve centerlines.

Magnet Composition and Performance. The magnets used for differentsystem embodiments 10 are comprised of a wide variety of magneticmaterials, such as suited for the desired thermal environment. In somepreferred embodiments of the electromagnetic valve system 10, thepermanent magnets 34 are comprised of neodymium. In some hightemperature engine environments, the permanent magnets 34 are comprisedof samarium cobalt.

In one embodiment, the present magnet 34, fully seated, with no air gap,provides a latching force of 124 pounds. In another embodiment, square(1.25 inch by 1.25 inch) stationary permanent magnets 34 provide alatching force of about 320 lbs.

In the electromagnetic valve system 10, the preferred use of permanentmagnets 34 having high magnetic flux properties provides light valvetrain mass, as well as corresponding fast valve train response times,such as stroke times approaching 1-2 milleseconds.

The dynamic mass 195 of the valve train includes both that of the valvespring 28 and the disable spring 30 for only a brief transition region193 in the center of travel, when both springs 28,30 are close to theirreleased free-length position, and where the kinetic energy of the valvetrain is high, and wherein the stored potential energy of the springs islow.

While some embodiments of the electromagnetic valve system 10 may have atransition length equal to zero, in most system embodiments, there is atransition region 193 greater than zero, such that a smooth energytransfer occurs between the first dynamic portion 195 and the seconddynamic portion 195, i.e. as energy is transferred between springs28,30.

Movement of the electromagnetic valve system 10 from the open position20 b to the closed position 20 a is similar to the actions required tomove the electromagnetic valve system from the closed position 20 b tothe open position 20 a. Electromagnetic energy is applied to thelatching electromagnetic coil 36, such that the stored potential energyin the valve spring 28 overcomes the latching force. The valve train 195moves toward the closed position 20 a, wherein energy may becontrollably applied to increase the attractive force at the closingend, as the disable spring is compressed. As before, energy to theelectromagnetic coil 36 may be applied at the closing end, to provide asoft landing in the closed position 20 a.

At either end of movement, additional energy may controllably be appliedby the electromagnetic coils, such as to compensate for friction withinthe system. For example. the applied energy may provide anelectromagnetic force which aids the permanent magnet to the latchposition, by pulling the clapper 26 into a latch position, within thelast portion of travel, in the closing and/or opening direction, e.g.for the last 0.010 to 0.020″.

Therefore, control of the electromagnetic valve system 10 is extremelyversatile, allowing: controlled opening and closing of a valve,independent of engine crankshaft position; assisted latch completionand/or release, and preferably providing a soft landing. Based oninformation from previous valve train movement, the electromagneticvalve system 10 can be dynamically adjusted, such as to after valvetiming and/or duration, and/or to adjust opening and/or closing energyparameters.

Electric Energy Storage. Some preferred embodiments of theelectromagnetic valve system 10 provide electrical energy exchangebetween the mechanical valve train and an energy storage system which isconnected to the electromagnetic coils, whereby the energy efficiency ofthe system is improved.

The energy storage module 370 shown in FIG. 41 preferably comprises anLC circuit 372, comprising an inductor 374 and a capacitor 376. Storedenergy from the capacitor 376 is released from the circuit to theelectromagnetic coil 36. Similarly, excess system energy is recoveredfrom the electromagnetic coil 36, by storage into the capacitor 76. Inconditions where the electromagnetic valve system needs more energy,more energy is applied to the capacitor 376, such that the increasedenergy 356 is released to the electromagnetic coil 356.

In some system embodiments 10, the electrical oscillation 378 of the LCcircuit is preferably matched to the mechanical oscillation of the valvetrain 10. Based on system operation, the proper level of energy storedin the capacitor 376 is adjusted.

Feed Forward and Feed Backward Control. The electromagnetic valve system10 is preferably controllable for steady state operation as well as forchanging operation conditions. For example, for conditions which requiremore or less torque, the operation curves of valve timing and/orduration are readily controlled.

In some system embodiments, a map is provided and stored of the dynamiccharacteristics of the engine under different controllable parameters.Based upon the map and desired engine operation, the controller 302 mayreadily change the operating parameters of the electromagnetic valvesystem 10, to achieve the desired result.

Overview of Electromagnetic Valve Systems Having Permanent MagnetLatching. FIG. 42 is a schematic diagram of generic structures andfunctionality throughout different embodiments of electromagnetic valvesystems 10. As seen in FIG. 42, the electromagnetic valve system 10generally comprises:

-   -   a valve assembly 12 which is linearly movable between a first        closed position 20 a and a second open position 20 b;    -   a spring assembly 405, e.g. such as a valve spring 28 and a        disable spring 30, in communication with the valve assembly 12,        wherein the spring assembly has a first spring assembly        position, when the valve assembly 12 is in the first closed        position 20 a, and a second spring assembly position when the        valve assembly 12 is in the second open position 20 b;    -   an electromagnet assembly 406, such as comprising one or more        electromagnets 36; and    -   a permanent magnet system 404, such as one or more permanent        magnets 34, and/or a clapper 26 at least partially comprising a        permanent magnetic material;    -   wherein the magnetic field from the permanent magnet system 404        provides an attractive latching force 408, e.g. 408 a,408 b to        valve assembly 12 when the valve assembly 12 is in any of the        first closed position 20 a and the second open position 20 b.

As seen in FIG. 1, the permanent magnet system 404 in electromagneticvalve system 10 a may preferably comprise both a permanent magnetclapper 26 affixed to the valve 12, as well as permanent magnets 34 a,34 b.

As seen in FIG. 33 and FIG. 34, the permanent magnet system 404 inelectromagnetic valve system 10 e comprises both stationary lower andupper permanent magnets 34 a, 34 b, as well as central magnetic circuits196 a,196 b, which conduct magnetic energy, such as to aid in movementand/or latching 408 of the clapper 26.

As seen in FIG. 36 and FIG. 37, the permanent magnet system 404 inelectromagnetic valve system 10 f comprises a single permanent magnet34, as well as pole blocks 212,214, which conduct magnetic energy, suchas to aid in movement and/or latching 408 of the clapper 26.

As seen in FIG. 38, the permanent magnet system 404 in electromagneticvalve system 10 g comprises both stationary lower and upper permanentmagnets 34 a, 34 b, such as to aid in movement and/or latching 408 ofthe clapper 26.

As seen in FIG. 39, the permanent magnet system 404 in electromagneticvalve system 10 h comprises a permanent magnet clapper 26 affixed to thevalve 12, which latches 408 to electromagnetic coil 36 b when the valve12 is located at the closed position 20 a, and latches 408 toelectromagnetic coil 36 a when the valve 12 is located at the openposition 20 b.

As seen in FIG. 42 and FIG. 43, the permanent magnet system 404 inelectromagnetic valve system 10 i comprises a permanent magnet 34 andone or more magnetically conductive armatures or yokes 453, whichconduct magnetic energy, such as to aid in movement and/or latching 408of the clapper 26.

In some system embodiments magnetic field from the permanent magnetsystem 404 provides a permanent magnet latching force 408, e.g. 408a,408 b, to the valve assembly 12 which is sufficient to hold the valveassembly 12 is in any of the first closed position 20 a and the secondopen position 20 b. In other system embodiments, energy can be suppliedto the electromagnetic system 406, to help latch the valve assembly 12in any of the first closed position 20 a and the second open position 20b, such as but not limited to compensation for diminished strength ofthe permanent magnet system 404.

Presently Preferred Embodiment of the Invention. FIG. 43 is a cutawayview 450 of an electromagnetic valve actuation system 10 i comprisingdiscrete spring and electromagnet assemblies, with the valve 12 in aclosed position 20 a. FIG. 44 is a top schematic view 460 of anelectromagnetic valve actuation system 10 i comprising discrete springand electromagnet assemblies 36 a, 36 b. While two electromagnets areshown, a single electromagnet may be used. In the preferred embodiment,both electromagnets are actuated together.

A spring keeper 192 affixed to the valve stem 14 moves linearly totransfer energy between the disable spring 30 and the valve spring 28. Aclapper 26 affixed to the valve stem 14 moves between a magnet assembly34 and electromagnet assemblies 36 a, 36 b. In this embodiment, thevalve stem is a compound structure that has a portion with a threadedend that engages with another portion that has complementary threads.The magnet assembly 34 comprises a permanent magnet. Note that in someembodiments, both a north pole of the permanent magnet and a south poleof the permanent magnet are used to attract or repel the electromagnet.

As seen in FIG. 43, the springs 28,30 are preferably fastened by theirends farthest from the keeper 192, and are not fastened to the springkeeper 192, such that the springs 28,30 are preferably isolated from thedynamic mass of the valve system 10 i during a portion of the valvemovement. In one exemplary embodiment, the springs 28,30 are rated at660 lbs./per inch. In the electromagnetic valve system 10 i, the valvestem shaft is non-magnetic.

The permanent magnet 34 provides a latching means for the clapper 26, ineither the closed position 20 a or the open position 20 b. As seen inFIG. 43, the permanent magnet 34 holds the valve spring 28 compressed inthe valve open position 20 b, whereby the valve spring 28 retains a highlevel of potential energy.

From the closed position 20 a, wherein the clapper 26 is latched againstthe poles encompassing permanent magnet 34, an applied energy to theelectromagnets 36 a, 36 b is controllably energized to release theclapper from the closed position 20 a. Upon activation of energy to theelectromagnets 36 a, 36 b, an electromagnetic flux is generated by theelectromagnets 36 a, 36 b, which opposes the permanent magnet flux ofthe permanent magnet 34. When the applied opposing electromagnetic fluxreduces the permanent magnet holding force below that of the springforce applied by the disable spring 30, the valve 12 begins to open.

As the valve 12 begins to open, the applied force of the permanentmagnet 34, which has a constant flux, is reduced. As the valve 12 opensand the clapper 26 moves away from the permanent magnet 34, whereby theapplied flux density from the permanent magnet 34 falls off veryrapidly, such that the attractive force decreases rapidly.

As the spring keeper 192 moves and advances toward the middle region193, the spring forces are equal, and the kinetic energy of the systemreaches a maximum. The spring keeper 192 continues to move, a wherebythe kinetic energy of the moving mass of the assembly is converted tostored potential energy in the valve spring 28. The moving mass of theassembly is typically equal to the combined mass of the clapper 26, thevalve 12, the keeper 192, and at least a portion of the springs 28,30.

In preferred embodiments of the electromagnetic actuation system 10, thekinetic mass of the valve train is minimized by the configuration of thevalve spring 28 and the disable spring 30, whereby kinetic energy istransferred between the valve spring 28 and the disable spring 30, in acentral region 193 of movement, and whereby the mass of either the firstor second spring 28,30 is substantially isolated from the effective massof valve train for a portion of movement.

For example, as seen in FIG. 43, as the spring keeper 192 moves beyondthe central region 193, the valve spring 28 is compressed by furtherdownward movement of the valve assembly, comprising the clapper 26, thevalve 12, and spring keeper 192, while the disable spring 30 becomesisolated from the assembly (FIG. 43).

When the valve assembly approaches the end of travel, e.g. such astoward an open position 20 b, the valve 12, clapper 26, and springkeeper 192 decelerate, as the kinetic energy of the valve assembly istransformed to stored potential energy in the valve spring 28. Near thelimit of travel, the applied flux from the electromagnets 36 a, 36 bprovide an attractive force to latch the valve 12 in the open position20 b.

As described above, the attractive force from between the permanentmagnet 34 and the electromagnets 36 a, 36 b is proportional to thedisplacement distance, i.e. there is a strong attractive force at thevery end region of travel. In preferred embodiments of the invention,therefore, energy may be controllably applied to the approachingelectromagnets 36 a, 36 b, to promote a ‘soft’ landing.

When the spring keeper 192 compresses the valve spring 28 to the bottomlimit of movement, i.e. wherein the clapper 26 approaches the armature453 of the electromagnets 36 a, 36 b, the clapper 26 contacts andlatches to the electromagnet assembly core because the magnet forceincreases as the clapper 26 approaches the electromagnets 36 a, 36 b. Atthe limit of travel, the magnetic holding force is larger than theopposing valve spring force, such that the valve 12 latches in the openposition 20 b. In the invention, the core 453 may be made of solid orlaminated materials. Where a laminated material is used for the core,the clapper may also be made of a laminate, preferably a continuousspiral to match the flux of the core. A laminated structure is lessexpensive to build and lighter in weight, and resists the generation ofeddy currents, which distort the flux distribution and lose energy. Inthis embodiment, the preferred permanent magnet has dimensions of3/16″×1½″×1½″.

In the electromagnetic valve system 10 i shown in FIG. 43 and FIG. 44,the valve 12 latches in either the closed position 20 a or in the openposition 20 b, with the application of minimal energy. In some preferredsystem embodiments 10 i, the latching is provided entirely by magneticenergy provided by the permanent magnet 34, such that no external energyis required to be applied to any of the electromagnets 36 a,36 b.

Release from either latch condition is controllable through appliedenergy signal, such as from an external control 302 (FIG. 40, FIG. 41).As seen in FIG. 41, an external controller 302 sends a signal, i.e.energy pulse, to the electromagnets 36 a, 36 b, which is latched to theclapper 26. The applied pulse overcomes the permanent magnet attractionforce, such that the compressed spring, e.g. the valve spring 28, actsupon the assembly, which moves toward the opposite position.

Mechanical Valve Disabler System. FIG. 45 is a detailed partialcross-sectional view of a valve disabler system 610 a. A valve 612 ismoveable in relation to a head 616 having a valve port 617. The valvecomprises a valve face 613 at a first end 611 a, which is sealable inrelation to a valve seat 615. The valve 612 also includes a valve stem614 which extends from the first end 611 a to a second end 611 b. Avalve cap 616 is located at the second end 611 b, such as a valve capassembly 616, e.g. comprising a cap & retainers.

A valve spring 618 provides a compressive force between the valve 612and a spring landing 620, which may be an integral portion of the head616. The valve spring 618 retains the valve 612 in a normally closedposition 21 a (FIG. 46) in relation to the head 616. When the valve 612extends toward an open position 21 b (FIG. 49), the compression of thevalve spring 618 provides a bias force against the valve cap 616.

A disable spring 622 is also affixed to the valve cap 616, and providestension to controllably open the valve 612. The disable spring 622 isalso affixed to a ring holder 624, such as by a first holder landing626. A cam spring 630 is located between the ring holder 624, such as bya second holder landing 628, and controllably provides a compressiveforce between the ring holder 624 and a movable cam cap 632. A rotatablecamshaft 634, having a cam lobe 636, controllably acts upon the cam cap632, to compress the cam spring 630.

The valve disabler system 610 a includes a disabler latch 640, which ismovable between an unlatched, i.e. valve enabled, position 652 a, and alatched, i.e. valve disabled, position 652 b. In FIG. 45, the disablerlatch 640 is in a latched position, such that rotation of the camshaft634 does not result in movement of the valve 612 toward an open position21 b (FIG. 49).

FIG. 46 is a partial cutaway view 660 of a valve disabler system 610 ain an uncompressed, disabled state 662. FIG. 47 is a partial cutawayview 670 of a valve disabler system 610 a in a compressed, disabledstate 672. As seen in FIG. 46 and FIG. 47, when the ring holder 624 isconfined by the latched position 652 b by the disable latch 640,rotation of the camshaft 634 does not result in the opening of the valve612.

As seen in FIG. 47, the cam lobe profile 636 acts to push the cam cap632 from a top position 650 a toward a lower position 650 b, whichcompresses the cam spring 630. However, the ring holder 624 is preventedfrom vertical movement, by the disable latch 640 being located in thelocked position 652 b. During disablement 652 b, the valve 612 remainsclosed 21 a.

FIG. 48 is a partial cutaway view 680 of a valve disabler system 610 ain an uncompressed, enabled state 682. FIG. 49 is a partial cutaway view690 of a valve disabler system 610 a in a compressed, enabled state 692.As seen in FIG. 48 and FIG. 46, when the ring holder 624 is notconfined, due to the enabled position 652 a of the disable latch 640,rotation of the camshaft 634 results in the opening 21 b of the valve612.

As seen in FIG. 49, the cam lobe profile 636 acts to push the cam cap632 from a top position 650 a toward a lower position 650 b, whichcompresses the cam spring 630. When the disable latch 640 is in theenable position 652 a, the ring holder 624 is allowed to movevertically.

As seen in FIG. 46, as the camshaft 634 rotates, the extended loberegion 636 of the camshaft 634 acts upon the cam spring cap 632 and camspring 630, to compress the cam spring 630. The ring holder 624, whichis in contact with the second lower end of the cam spring 630, movesdownward in reaction to the compressive force from the cam spring 630,since the disable latch 640 is in the open “valve enabled” position 652a. The lower end of the disable spring 622 is also connected to the ringholder 624, such that the reactive downward movement of the ring holdercreates tension in the disable spring 622. The valve 612 is verticallyaffixed to the upper second end of the disable spring 622, such that thevalve opens 21 b in reaction to tension in the disable spring 622,whereby the valve face 613 extends from the valve seat 615.

Alternate Mechanical Valve Disabler System. FIG. 50 is a detailedpartial cross-sectional view 700 of an alternate mechanical valvedisabler system 610 b in a first position with a disabler set. FIG. 51is a detailed partial cross-sectional view 710 of an alternatemechanical valve disabler system 610 b in a second disabled positionwith a disabler set. FIG. 52 is a detailed partial cross-sectional view720 of an alternate mechanical valve disabler system 610 b in a firstenabled and closed position. FIG. 53 is a detailed partialcross-sectional view 730 of an alternate mechanical valve disablersystem 610 b in a second enabled and opened position.

Disabler Details. FIG. 54 is a detailed partial cross-sectional view 740of a spring disabler mechanism 742 in contact with a valve cap 744located between a valve spring 28 and a disable spring 30. FIG. 55 is aschematic profile 770 of a disabler cam lobe 772.

The lobe 772 is preferably designed to accelerate the disable spring 30and disable spring holder down with just enough forced delivered duringapproximately one sixth turn of a camshaft 34, so as to reach a fullycompressed position with zero speed (as is done with the conventionalcamshaft/poppet valve system). In some embodiments, ¼ revolution issufficient, since no deceleration is required.

The disabler solenoid 742 is released as soon as the disabler springholder 744 begins to move downward, allowing the clapper to move alongthe outer surface of the holder. When the disabler spring holder reachesthe lower zero speed point, the rebound spring pushes the clapper alongthe outer surface of the holder, locking it in place.

FIG. 54 shows the angled locking surface for both the valve cap anddisabler spring holder. The angle theta of the surface determines theproportion of the disabler spring force, where Fx=Fz sine theta, whichthe solenoid spring must exert, to prevent the disabler spring frompushing up the holder.

The solenoid, when energized, overcomes the solenoid spring force, andallows the disabler spring holder to move up. The disabler spring isrestrained from moving up to hold the spring compressed. The lobesurface restrains the holder in the up position.

Although the valve disabler system and its methods of use are describedherein in connection with an engine, such as an internal combustionengine, the apparatus and techniques can be implemented for a widevariety of alternate internal combustion and/or hybrid engines, or anycombination thereof, as desired. Furthermore, the apparatus andtechniques can be implemented for a wide variety of valves and/oractuators, or any combination thereof, as desired.

Accordingly, although the invention has been described in detail withreference to a particular preferred embodiment, persons possessingordinary skill in the art to which this invention pertains willappreciate that various modifications and enhancements may be madewithout departing from the spirit and scope of the claims that follow.

1. A valve system, comprising: a valve assembly linearly movable betweena first closed position and a second open position; a spring assembly incommunication with the valve assembly having a first spring assemblyposition when the valve assembly is in the first closed position and asecond spring assembly position when the valve assembly is in the secondopen position; at least one first electromagnet; and at least onepermanent magnet; wherein the magnetic field from at least one of thepermanent magnets provides an attractive latching force to valveassembly when the valve assembly is in any of the first closed positionand the second open position.
 2. The valve system of claim 1, whereinthe permanent magnet comprises a permanent magnet clapper fixedlyattached to the valve assembly.
 3. The valve system of claim 1, whereinthe valve assembly further comprises a magnetically conductive clapperfixedly attached to the valve assembly.
 4. The valve system of claim 3,further comprising: magnetically conductive material in contact with thepermanent magnet, whereby the magnetically conductive clapper latches tothe magnetically conductive material when the valve assembly is in anyof the first closed position and the second open position.
 5. The valvesystem of claim 1, wherein the a spring assembly comprises a firstspring and a second spring, wherein the first spring is compressed bythe valve assembly when the valve assembly is located in the secondposition, and is uncompressed when the valve assembly is located in thefirst position; and wherein the second spring is compressed by the valveassembly when the valve assembly is located in the first position, andis uncompressed when the valve assembly is located in the secondposition.
 6. The valve system of claim 5, wherein said first spring isisolated from the valve assembly at the first closed position, andwherein said second spring is isolated from the valve assembly at thesecond open position.
 7. The valve system of claim 5, wherein the firstspring and the second spring each have a different rate of compression.8. The valve system of claim 5, wherein the first spring and the secondspring have different lengths.
 9. The valve system of claim 5, whereinthe first spring and the second spring have different masses.
 10. Thevalve system of claim 1, further comprising: means for providing energyto at least one of the electromagnets to increase a local magneticfield.
 11. The valve system of claim 1, further comprising: means forproviding energy to at least one of the electromagnets to decrease alocal magnetic field.
 12. The valve system of claim 1, furthercomprising: means for providing energy to at least one of theelectromagnets to attract the valve assembly.
 13. The valve system ofclaim 1, further comprising: means for providing energy to at least oneof the electromagnets to repel the valve assembly.
 14. The valve systemof claim 1, further comprising: means for repelling and attracting thevalve assembly to allow the valve assembly to be opened and/or closedmore quickly than a natural frequency of the spring assembly wouldperform while still obtaining a soft landing.
 15. The valve system ofclaim 1, further comprising: means for feedback control of valveassembly motion.
 16. The valve system of claim 15, wherein the feedbackcontrol compensates for any of friction forces and pressure forces. 17.The valve system of claim 1, further comprising: means for energyrecovery during deceleration of said valve assembly.
 18. The valvesystem of claim 1, wherein the attractive latching force is sufficientto hold the valve assembly in any of the first closed position and thesecond open position, such that no external power is required to holdthe valve assembly in any of the first closed position and the secondopen position.
 19. The valve system of claim 1, further comprising:means for storing energy recovered from at least one of theelectromagnets.
 20. The valve system of claim 1, wherein at least one ofthe permanent magnets comprises any of neodymium and samarium cobalt.21. The valve system of claim 1, wherein both a north pole and a southpole of at least one of the permanent magnets are used to attract orrepel the valve assembly.
 22. The valve system of claim 1, furthercomprising: an electromagnetic assembly core which extends from theelectromagnet.
 23. The valve system of claim 22, wherein theelectromagnetic assembly core comprises any of a solid material and alaminated material.
 24. The valve system of claim 22, wherein theelectromagnetic assembly core comprises a laminated material, andwherein the valve assembly comprises a clapper fixedly attached to thevalve assembly, the clapper comprising a laminated material.
 25. A valvesystem, comprising: a valve assembly linearly movable between a closedposition and an open position; a spring assembly associated with thevalve assembly having a fist spring assembly position when the valve isin the first closed position and a second spring assembly position whenthe valve is in the second open position; at least one electromagnet; aclapper affixed to the valve assembly and movable in relation to theelectromagnet; and at least one permanent magnetic latch having amagnetic field, wherein the magnetic field from the permanent magneticlatches provides an attractive latching force to the clapper when thevalve assembly is in any of the closed position and the open position.26. The valve system of claim 25, further comprising: means forproviding energy to at least one of the electromagnets to increase alocal magnetic field.
 27. The valve system of claim 25, furthercomprising: means for providing energy to at least one of theelectromagnets to decrease a local magnetic field.
 28. The valve systemof claim 25, further comprising: means for providing energy to at leastone of the electromagnets to attract the clapper.
 29. The valve systemof claim 25, further comprising: means for providing energy to at leastone of the electromagnets to repel the clapper.
 30. The valve system ofclaim 25, wherein the clapper comprises a permanent magnet.
 31. Thevalve system of claim 25, further comprising: means for repelling andattracting the valve assembly to allow the valve assembly to be openedand/or closed more quickly than a natural frequency of the springassembly would perform while still obtaining a soft landing.
 32. Thevalve system of claim 25, further comprising: means for feedback controlof valve assembly motion.
 33. The valve system of claim 32, wherein thefeedback control compensates for any of friction forces and pressureforces.
 34. The valve system of claim 25, further comprising: means forenergy recovery during deceleration of said valve assembly.
 35. Thevalve system of claim 25, wherein the attractive latching force issufficient to hold the valve assembly in any of the first closedposition and the second open position, such that no external power isrequired to hold the valve assembly in any of the first closed positionand the second open position.
 36. The valve system of claim 25, furthercomprising: means for storing energy recovered from at least one of theelectromagnets.
 37. The valve system of claim 25, wherein the permanentmagnet latches comprises any of neodymium and samarium cobalt.
 38. Thevalve system of claim 25, wherein the a spring assembly comprises afirst spring and a second spring, wherein the first spring is compressedby the valve assembly when the valve assembly is located in the secondposition, and is uncompressed when the valve assembly is located in thefirst position; and wherein the second spring is compressed by the valveassembly when the valve assembly is located in the first position, andis uncompressed when the valve assembly is located in the secondposition.
 39. The valve system of claim 38, wherein the first spring isisolated from the valve assembly at the closed position, and wherein thesecond spring is isolated from the valve assembly at the open position.40. The valve system of claim 38, wherein the first spring and thesecond spring each have a different rate of compression.
 41. The valvesystem of claim 38, wherein the first spring and the second spring havedifferent lengths.
 42. The valve system of claim 38, wherein the firstspring and the second spring have different masses.
 43. The valve systemof claim 25, wherein energy is returned to a power source by use ofregenerative breaking of the clapper.
 44. The valve system of claim 25,wherein both a north pole and a south pole of at least one of thepermanent magnet latches are used to attract or repel the clapper. 45.The valve system of claim 25, further comprising: a software module forat least partially controlling a soft landing and optionally forreducing power consumption.
 46. The valve system of claim 25, furthercomprising: means to open the valve partially and close the valve again.47. The valve system of claim 25, further comprising: an electromagneticcore.
 48. The valve system of claim 47, wherein the electromagnetic coreis formed as a laminated structure.
 49. The valve system of claim 25,wherein the clapper is formed as a spiral laminate structure.
 50. Thevalve system of claim 25, wherein the clapper comprises at least onepermanent magnet which provides at least a portion of the magnetic fieldfor the permanent magnetic latches.